Proportional pressure control valve

ABSTRACT

The invention relates to a proportional pressure control valve comprising a valve box ( 10 ) which has at least three fluid-carrying connections, especially in the form of a pump (P), a user (A) and a reservoir (T) connection, a control piston ( 18 ) being guided in a longitudinally displaceable manner inside the valve box ( 10 ) for optionally connecting the pump connection (P) to the user connection (A) and the user connection (A) to the reservoir connection (T). A fluid-carrying connection is established between the pump connection (P) and a pilot chamber ( 20 ) of a pilot valve ( 22 ), the pilot valve ( 22 ) being controlled by a magnet system, especially a proportional magnet system ( 28 ). The proportional pressure control valve according to the invention is characterized in that the fluid-carrying connection to the pilot chamber ( 20 ) has a bore ( 27 ) that runs axially inside the wall of the valve box ( 10 ) and extends from a radial bore ( 9 ) of the housing ( 10 ) forming the pump connection (P).

The invention relates to a proportional pressure control valve comprising a valve housing which has at least three fluid-conducting connections, particularly in the form of a pump connection, a user connection, and a tank connection, a control piston being guided to be able to move lengthwise within the valve housing for selective connection of the pump connection to the user connection and of the user connection to the tank connection, there being a fluid-conducting connection between the pump connection and a pilot chamber of a pilot valve, and the pilot valve being controllable by a magnet system, in particular a proportional magnet system.

For applications in which large volumetric flows are controlled, pilot-controlled pressure control valves are preferably used instead of directly controlled valves. A high volumetric flow means both large opening cross sections of the valves for large strokes and large flow forces which counteract the magnetic force of the magnet system to be actuated as a disturbance variable. To resolve these problems, the magnet system would have to be dimensioned to be correspondingly large for directly controlled valves.

Therefore, for applications of this type, valves are known in the prior art which have hydraulic piloting, see DE 103 25 178 A1. This known solution is characterized, compared to other proposed solutions which are prior art and which are disclosed by U.S. Pat. No. 6,286,535 B1, in that the valve is able to set a pressure value of 0 bar on the user connection when the magnet system is not actuated. For the valves disclosed in the US patent, this is not possible because, according to their construction, the control piston is returned to its end position by means of a clamped compression spring when the magnet system has not been actuated. Due to this mechanical configuration, these valves still have a pressure level which corresponds to the force of the clamped spring when there is no electrical control signal of the magnet system present.

With respect to the prior art, the object of the invention is to further develop a proportional pressure control valve which can be set according to the solution according to DE 103 25 178 A1 on the user connection to a residual pressure of 0 bar such that in contrast it is characterized by a simpler and more compact construction.

According to the invention, this object is achieved by a proportional pressure control valve which has the features of claim 1 in its entirety.

One important feature of the invention is accordingly that the fluid-conducting connection to the pilot chamber is integrated essentially completely into the valve housing by a bore which runs in the axial direction being formed in its wall and emerging from a radial bore of the valve housing which forms the pump connection. In the latter known solution, to form the fluid-conducting connection the control piston is provided with an inner connecting channel which, before discharging into the pilot chamber, has an orifice to which a flow diffusor is connected downstream and a protective screen is connected upstream. For the control piston this yields not only a comparatively complex construction, but also a considerable installation length, as a result of which in turn a corresponding installation length of the valve housing is dictated. The valve according to the invention is, in contrast, characterized by the desired compact and simplified construction.

In another advantageous configuration, according to the invention the user connection can be formed by the coaxial, end-side opening of the valve housing. This yields the especially advantageous possibility of further reducing the installation length, because, offset in the longitudinal direction of the valve housing, on the latter only two connections through which flow takes place radially need be formed by radial bores, specifically the pump connection and the tank connection, so that the control piston need have a correspondingly smaller number of peripheral control edges; this in turn allows simplification and a reduction in the required installation length.

Advantageously, the control piston can have, as a movable boundary of the pilot chamber, a closed, planar piston surface which lies in one radial plane.

Here the arrangement can be advantageously made such that a valve body of the pilot valve, which body is located stationary in the valve housing, forms a further, stationary boundary of the pilot chamber and the end section of the fluid-conducting connection to the pilot chamber, which section is remote from the pump connection.

In these exemplary embodiments, the arrangement can be made such that the end section of the fluid-conducting connection contains a radial channel which extends between an inner coaxial bore of the valve body and an annular gap which, between the peripheral surface of the valve body and the valve housing, forms a filtration gap into which the end of the radial bore of the valve housing discharges. This design likewise contributes to a compact structure because the installation of the protective filter for the pilot fluid does not necessitate any additional axial installation length.

Other advantageous configurations of the proportional pressure control valve according to the invention are the subject matter of the other dependent claims 6 to 11.

Since, as mentioned, a valve system is devised in which it can be ensured that on the user connection a pressure value of 0 bar is set without the magnet system actuated, the invention is especially well suited for use in hydraulically actuated clutches, for whose operational reliability it is essential that when the clutch is released, the clutch packs or disk packs which are engaged are reliably separated from one another. According to claim 12, the subject matter of the invention is therefore also the use of the valve according to the invention for hydraulically actuatable clutches.

The invention is detailed below using the exemplary embodiments shown in the drawings.

FIG. 1 shows partially in a front view, partially in a longitudinal section, a proportional pressure control valve according to the prior art;

FIGS. 2 to 4 show drawings of a first exemplary embodiment of the proportional pressure control valve according to the invention drawn likewise partially in a front view, partially in a longitudinal section, in different operating or actuating positions;

FIG. 5 shows a longitudinal section of a second exemplary embodiment of the proportional pressure control valve according to the invention which is drawn on a somewhat smaller scale compared to FIGS. 2 to 4;

FIG. 6 shows a partial longitudinal section of only the region designated in FIG. 5 with the dot-dash circle, enlarged compared to FIG. 5;

FIG. 7 shows in the manner of a simplified operating representation the use of a proportional pressure control valve according to the invention for the application in a multiple-disk clutch, and

FIG. 8 shows the progression of a clutch play process for a clutch valve arrangement according to the hydraulic arrangement from FIG. 7.

FIG. 1 shows a proportional pressure control valve of the prior art according to DE 103 25 178 A1. The valve has, designed as a screw-in cartridge, a valve housing 10 which can be screwed into a machine part which is not detailed, for example, in the form of a valve block 3, via a screw-in section 12. For the sealed connection to the valve block 3, the valve housing 10 accordingly has gaskets 14 on the outer peripheral side which are seated in the corresponding receivers. The valve housing 10, viewed in the direction of looking at FIG. 1, from top to bottom has radial bores 5 for a tank connection T, radial bores 7 for a user connection A, and radial bores 9 for a pump connection P for a hydraulic pump 16 (cf. FIG. 7). Furthermore, within the valve housing 10 a control piston 18 is movably guided lengthwise for selective connection of the pump connection P to the user connection A and of the user connection A to the tank connection T.

To establish a fluid-conducting connection between the pump connection P and a pilot chamber 20 of a pilot valve designated as a whole as 22, the control piston 18 is provided with a connecting channel 24 which is coaxial to the longitudinal axis 26 and which, offset in its end section, is the bottom one in FIG. 1 that leads to a radial bore 9 of the pump connection P and is connected in its upper end section to the pilot chamber 20 via an outlet system 15. The outlet system 15 contains an orifice to which in the fluid flow direction a protective screen is connected upstream and a so-called diffusor is connected downstream, which latter is used preferentially to deflect the directed oil jet which flows out of the orifice so that it does not directly strike the movable closing part 40 of the pilot valve 22.

The pilot valve 22 has a stationary valve body 42 in which an inner, coaxial bore 11 is open, on the one hand, toward the pilot chamber 20 and, on the other hand, on the opening edge it has a seat 13 for the movable closing part 40 of the pilot valve 22. Said valve can be actuated via a magnet system which is designated as a whole as 28, in particular in the form of a proportional magnet system. If said magnet system is energized, its actuating plunger 32 is moved downward in the figure, as a result of which the closing part 40 is pressed against the valve seat 13 via a spring arrangement 17 with a closing force which is dependent on the intensity with which the magnet system 28 is energized in order to close the pilot valve 22.

If the proportional magnet system 28 remains deenergized, hydraulic medium (oil) can flow from the user connection A to the tank connection T. In this valve state, therefore the pilot valve 22 is open and the control piston 18 is moved onto its upper stroke stop against the lower side of the valve body 42. In this operating position, the oil flows from the pump connection P through the control piston 18 to the pilot chamber 20 and from there via the opened pilot valve 22 to a distributor chamber 19 from which it drains via channels 58 to the tank connection T. This volumetric flow can be defined as a pilot oil flow or leakage.

When current is supplied to the magnet system 28, the closing part 40 presses on the valve seat 13 and, in so doing, interrupts the volumetric flow. The pilot chamber 20 is thus filled with the hydraulic medium, as a result of which the pressure in this chamber rises. This rising pressure acts on the upper face side of the control piston 18 and moves it in the direction of the lower stroke stop 70 against the compressing compression spring 64. The pressure in the pilot chamber 20 then corresponds to the adjusted pressure.

When the closing pressure of the closing part 40 on the seat 13 of the valve body 42 closes the pilot valve 22 by energizing the magnet system 28, the pressure in the pilot chamber 22 rises to a pressure value at which the control piston 18 is moved downward in the figure against the main piston spring 64 until a position is reached in which the user connection A is connected to the pump connection P. When the controlled pressure is reached, the control piston 18 is moved such that the connection between the pump connection P and the user connection A is throttled. The control piston 18 is moved into a position in which the two force levels are in equilibrium with one another, and in this way it defines an opening window between the pump connection P and the user connection A. Therefore, a pressure is established on the user connection A, which is in a direct relationship to the electrical control signal of the magnet system 28.

FIGS. 2 to 4 illustrate a first exemplary embodiment of the proportional pressure control valve according to the invention. Parts which correspond to those of the valve from FIG. 1 are marked with the same reference numbers as in FIG. 1. The plunger of the magnet system 28, which plunger is not shown, acts via a pilot spring 21 on the closing part 40 of the pilot valve 22, which part is formed by a ball. As in the known solution according to FIG. 1, the closing part 40 interacts with a valve seat 13 which is located on the opening edge of an inner coaxial bore 11 of a stationary valve body 42. The bottom of the valve body 42 which faces away from the valve seat 13 forms the stationary boundary of the pilot chamber 20 and the upper stroke stop of the control piston 18, whose upper planar piston surface forms the movable boundary of the pilot chamber 20. The interior of the coaxial inner bore 11 of the valve body 42 is fluid-connected via a damping orifice 23 to the pilot chamber 20. This orifice 23 forms the end part of the fluid-conducting connection between the pump connection P and pilot chamber 20. The main part of the fluid-conducting connection is formed by an axial bore 27 which is made in the wall of the valve housing 10 and which has its origin on a radial bore 9 of the pump connection P. From here the axial bore 27 leads to the outer periphery of the stationary valve body 42 where the axial bore 27 undergoes transition into an annular gap 29. The latter forms a filtration gap between the end of the axial bore 27 and a radial channel 31 which leads in the valve body 42 via a control oil orifice 33 to the inner coaxial bore 11, whence the fluid connection via the damping orifice 23 to the pilot chamber 20 is completed.

FIG. 2 shows an operating state in which the magnet system 28 is not energized, the pilot valve 22 conversely is not closed, and thus a fluid pressure does not build up in the pilot chamber 20 because the fluid which has been supplied via fluid-conducting connection 27, 29, 31, 33 can drain via the distributor chamber 19 to the tank side. Accordingly, the control piston 18 is under the influence of the spring 64 in the upper end position where it adjoins the stroke stop, i.e., the bottom of the valve body 42. Since in the valve according to the invention only the tank connection T and the pump connection P are formed by radial bores 5 and 9 respectively, while the user connection A is formed by the coaxial, end-side opening 35 of the housing 10, in the operating position from FIG. 2 the user connection A and the tank connection T are connected to one another, specifically such that the control piston 18 has an interior which is open to the opening 35 of the valve housing 10, and from which fluid can emerge via passages 37 in the wall of the piston 18 to the tank connection T.

FIGS. 3 and 4 show operating states depending on the energizing of the magnet system 28. FIG. 3 shows the operating state in which the closing part 40 is pressed onto the valve seat 13 by energizing the magnet system 28 via the spring 21 so that in the pilot chamber 20 a pressure is built up which has moved the control piston 18 onto its lower stroke stop 70. As is apparent, in this piston position the pump connection P and the user connection A are connected to one another, and as is apparent likewise from FIG. 3, with large opening cross sections between the interior of the control piston 18 and the radial bores 9 being formed so that in an application to actuate a clutch cylinder, filling is prompt.

When a fill pressure of the consumer is reached, on the user connection A, for example, of the clutch cylinder, and when there is a force which acts in this way on the piston 18, said piston is pushed upward in the figure, see FIG. 4, until the connection from the pump connection P to the user connection A is throttled or completely blocked or, as likewise shown in FIG. 4, the user connection A and the tank connection T are connected to one another, with a piston position being established in which the piston is in force equilibrium. The illustrated valve construction is characterized by high dynamics and low pressure loss, as a result of which, when used for clutch actuation, rapid filling with oil and rapid evacuation of the clutch are ensured. The invention is therefore also especially well suited for these applications because in the deenergized state of the magnet system 28 the user connection A is completely relieved.

A second, modified exemplary embodiment of the valve according to the invention is shown in FIGS. 5 and 6. In the example of FIGS. 2 to 4 which was described first, the valve is subject to a certain leakage because in almost any operating state a control oil flow drains permanently to the tank. While the control oil orifice 33 keeps this leakage to a low value, it is still useful to reduce leakage losses. In the exemplary embodiment from FIGS. 5 and 6, for this purpose the piloting is configured such that, instead of a seat valve with spring-loaded closing part, a directly controlled pressure regulator is integrated into the piloting. Here the fluid-conducting connection, as in the above described exemplary embodiment, in the starting part is made by the axial bore 27 which runs in the wall of the valve housing 10 and which leads to the inner coaxial bore 11 in the valve body 42 via the peripheral annular gap 29 of the stationary valve body 42 and via a radial channel 31 located in it. Within the inner bore 11 a, valve piston 38 is guided to be able to move lengthwise and is held nonpositively on the plunger 32 of the magnet system 28 via a reset spring 39, and, when the magnet system 28 is energized, can be moved downward in the drawings. The valve piston 38 has a bore 41 which is open to the pilot chamber 20 and peripheral control edges 43, 44 which are connected to said bore so that, depending on the axial position of the valve piston 38, the radial channel 31 and thus the fluid-conducting connection to the pump connection P are connected to the pilot chamber 20 or are blocked. In the position in which the radial channel 31 is blocked, the pilot chamber 20 is opened to the distributor chamber 19 and thus to the tank via the axial piston bore 41 and the control edge 44. There is no direct connection from the pump connection P to the tank connection T in any operating state, and therefore the valve works without additional losses due to the draining pilot oil. The leakage is therefore reduced to the valve spool leakage, which occurs on the annular gaps of the peripheral surfaces of the two pistons.

The proportional pressure control valve according to the invention is one which is advantageous especially for clutch applications. In these applications, the main demands are for high dynamics and low pressure losses in order to be able to ensure a rapid process of filling with oil and a rapid evacuation of the clutch. This is easily accomplished with this valve configuration. Moreover, the valve according to the invention can be completely relieved; i.e., when the electrical control signal on the magnet system 28 is taken away, the controlled pressure on the user connection A is brought to the pressure value of 0 bar. In the otherwise conventionally pilot-operated pressure valves, this main stage (control piston) is returned with a clamped compression spring to its end position so that, when there is no electrical control signal on the magnet system, the known valves always have a pressure level that corresponds to the force of the clamped spring. The latter then leads to problems in the decoupling of hydraulically operating clutches.

To illustrate this, the use of the proportional pressure control valve according to the invention is detailed with reference to FIGS. 7 and 8 for a hydraulically operating clutch, according to the representation and FIG. 7 the proportional pressure control valve being connected between the clutch parts 72, 74, 76 and the hydraulic pump 16.

Clutches are used, among other things, to connect two shafts, for example the shafts of heavy machinery to transmission shafts. In this hydraulic clutch, a cylinder chamber 72 is connected to the pressure line or the pressure connection P of the hydraulic pump 16 by actuating the proportional pressure control valve according to the invention. In so doing, the spring-loaded piston 74 compresses a clutch disk pack which is not detailed. By switching over the proportional pressure control valve, the cylinder chamber 72 is then evacuated, and the compression spring arrangement 76 according to FIG. 7 pushes the piston 74 back into its initial position. In so doing, the remaining hydraulic medium is pushed out in the direction toward the tank T via the user connection A.

FIG. 8 shows the progression of a clutch play. First, the clutch must be quickly filled with oil (hydraulic medium). This takes place in the time interval t₁ to t₂, with the piston 74 thus beginning to compress the clutch disk pack. This process is accompanied by a brief, very high volumetric flow. Afterwards, this state is maintained in the time interval from t₂ to t₃ and is slowly “ramped up” in the interval t₃ to t₄ by the pressure being slowly raised linearly by the proportional pressure control valve according to the invention so that in this way the force from the heavy machinery is uniformly transmitted to the transmission line. At time t₅, by returning the electrical control signal on the magnet system 28, the pressure in the clutch is removed so that the compressed disk pack, under additional action of the compression spring arrangement 76, can push the piston 74 back into its original position again; this is easily possible since as already shown the pressure value on the connection A has the value 0 in this operating position. 

1. A proportional pressure control valve comprising a valve housing (10) which has at least three fluid-conducting connections, particularly in the form of a pump (P) connection, a user (A) connection, and a tank (T) connection, a control piston (18) being guided to be able to move lengthwise within the valve housing (10) for selective connection of the pump connection (P) to the user connection (A) and of the user connection (A) to the tank connection (T), with there being a fluid-conducting connection between the pump connection (P) and a pilot chamber (20) of a pilot valve (22), and the pilot valve (22) being controllable by a magnet system, in particular a proportional magnet system (28), characterized in that the fluid-conducting connection to the pilot chamber (20) has a bore (27) which runs in the axial direction within the wall of the valve housing (10) and which emerges from a radial bore (9) of the housing (10) which forms the pump connection (P).
 2. The proportional pressure control valve according to claim 1, characterized in that the user connection (A) is formed by the coaxial, end-side opening (35) of the valve housing (10).
 3. The proportional pressure control valve according to claim 1, characterized in that the control piston (18) has as a movable boundary of the pilot chamber (20) a closed, planar piston surface which lies in one radial plane.
 4. The proportional pressure control valve according to claim 3, characterized in that a valve body (42) of the pilot valve (22), which body is arranged stationary in the valve housing (10), forms a further, stationary boundary of the pilot chamber (20) and the end section of the fluid-conducting connection to the pilot chamber (20), which section is remote from the pump connection (P).
 5. The proportional pressure control valve according to claim 4, characterized in that the end section of the fluid-conducting connection contains a radial channel (31) which extends between an inner coaxial bore (11) of the valve body (42) and an annular gap (29) which forms, between the peripheral surface of the valve body (42) and the valve housing (10), a filtration gap into which the end of the axial bore (27) of the valve housing (10) discharges.
 6. The proportional pressure control valve according to claim 4, characterized in that in the valve housing (10) there is a distributor chamber (19) which borders the end of the valve body (42) which faces away from the pilot chamber (20), which is connected to the tank connection (T), and which accommodates the fluid flowing through the pilot valve (22).
 7. The proportional pressure control valve according to claim 4, characterized in that on the edge of the inner bore (11) of the valve body, which edge faces away from the pilot chamber (20), a seat (13) is formed for a movable closing element (40) which is pretensioned by a pilot spring (21) into contact with the seat (13).
 8. The proportional pressure control valve according to claim 5, characterized in that the radial channel (31) of the valve body (42) discharges via an orifice (33) into the inner coaxial bore (11).
 9. The proportional pressure control valve according to claim 8, characterized in that the coaxial inner bore (11) of the valve body (42) is connected via a damping orifice (23) to the pilot chamber (20).
 10. The proportional pressure control valve according to claim 4, characterized in that in the inner coaxial bore (11) of the valve body (42) a pilot piston (38) can be axially moved and forms an adjustable pressure regulator for the pilot chamber (20).
 11. The proportional pressure control valve according to claim 1, characterized in that an energy storage mechanism, in particular in the form of a spring (64), acts on the end of the control piston (18) facing away from the pilot chamber (20) and tries to move the control piston (18) in the direction toward the pilot chamber (20).
 12. Use of the proportional pressure control valve according to claim 1 for hydraulically actuatable clutches in which a cylinder chamber (72) of the clutch can be connected to a hydraulic pump (16) via the valve to compress a disk pack. 